CN107781360B - power shift transmission system - Google Patents
power shift transmission system Download PDFInfo
- Publication number
- CN107781360B CN107781360B CN201711222479.3A CN201711222479A CN107781360B CN 107781360 B CN107781360 B CN 107781360B CN 201711222479 A CN201711222479 A CN 201711222479A CN 107781360 B CN107781360 B CN 107781360B
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- Prior art keywords
- gear
- oil
- liquid filling
- box body
- hydraulic friction
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 45
- 230000007704 transition Effects 0.000 claims abstract description 24
- 239000003921 oil Substances 0.000 claims description 71
- 239000007788 liquid Substances 0.000 claims description 26
- 239000010687 lubricating oil Substances 0.000 claims description 18
- 239000012530 fluid Substances 0.000 claims description 8
- 238000007789 sealing Methods 0.000 claims description 6
- 230000001050 lubricating effect Effects 0.000 claims 1
- 230000007246 mechanism Effects 0.000 description 22
- 238000005461 lubrication Methods 0.000 description 5
- 238000005192 partition Methods 0.000 description 3
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 230000004044 response Effects 0.000 description 2
- 230000001360 synchronised effect Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/089—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears all of the meshing gears being supported by a pair of parallel shafts, one being the input shaft and the other the output shaft, there being no countershaft involved
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/042—Guidance of lubricant
- F16H57/0421—Guidance of lubricant on or within the casing, e.g. shields or baffles for collecting lubricant, tubes, pipes, grooves, channels or the like
- F16H57/0424—Lubricant guiding means in the wall of or integrated with the casing, e.g. grooves, channels, holes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
- F16H61/0262—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being hydraulic
- F16H61/0265—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being hydraulic for gearshift control, e.g. control functions for performing shifting or generation of shift signals
- F16H61/0267—Layout of hydraulic control circuits, e.g. arrangement of valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H2003/0818—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts comprising means for power-shifting
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention belongs to the field of diesel engine power output system design, and in particular relates to a power shift transmission system which comprises a box body, a first input shaft and a first output shaft, wherein a first driving gear and a second driving gear are arranged on the first input shaft; the first output shaft is provided with a first driven gear and a second driven gear, and a first transition gear is also arranged in the box body; the first driving gear and the second driving gear respectively form clutch transmission with the first input shaft through a first hydraulic friction clutch and a second hydraulic friction clutch, and the first driven gear and the second driven gear respectively form clutch transmission with the first output shaft through a third hydraulic friction clutch and a fourth hydraulic friction clutch. The invention provides a novel gearbox clutch system which can realize the forward and reverse rotation adjustment of a clutch output shaft and the rotation speed adjustment of the output shaft.
Description
Technical Field
The invention belongs to the field of diesel engine power output system design, and particularly relates to a power shift transmission system.
Background
The gear box is an indispensable power output device of the motor vehicle, and the main function of the gear box is to transmit the power output by the engine according to different transmission ratios so as to realize the large-scale speed regulation. For agricultural or engineering vehicles, the vehicles are generally required to have more gears than household vehicles, so that the diesel engine gearbox in the prior art is complex in structural design, low in response speed during gear shifting and incapable of meeting actual use requirements.
Disclosure of Invention
The invention aims to provide a power shift transmission system with more flexible gear shift and faster gear shift response speed.
In order to achieve the above purpose, the present invention provides the following technical solutions: the power gear shifting transmission system comprises a box body, a first input shaft and a first output shaft, wherein the first input shaft and the first output shaft are respectively arranged on a bearing seat in the box body in a rotating way through bearings, a first driving gear and a second driving gear are arranged on the first input shaft, the first driving gear is a single gear, and the second driving gear is a duplex gear; the first output shaft is provided with a first driven gear and a second driven gear, wherein the first driven gear is a duplex gear, the second driven gear is a single gear, and a first transition gear is also arranged in the box body; the first driving gear is meshed with a left side gear of the first driven gear, the left side gear of the second driving gear is meshed with a right side gear of the first driven gear, the right side gear of the second driving gear is meshed with a first transition gear, and the first transition gear is meshed with a second driven gear; the first driving gear and the second driving gear respectively form clutch transmission with the first input shaft through a first hydraulic friction clutch and a second hydraulic friction clutch, and the first driven gear and the second driven gear respectively form clutch transmission with the first output shaft through a third hydraulic friction clutch and a fourth hydraulic friction clutch.
The invention has the technical effects that: the invention provides a novel gearbox clutch system which can realize the forward and reverse rotation adjustment of a clutch output shaft and the rotation speed adjustment of the output shaft.
Drawings
FIG. 1 is a general assembly view of a powershift transmission provided by an embodiment of the present invention;
FIG. 2 is a partial view of a clutch transmission provided by an embodiment of the present invention;
FIG. 3 is an enlarged partial view of I of FIG. 2;
fig. 4 is a schematic perspective view of a case according to an embodiment of the present invention;
FIG. 5 is a cross-sectional view of a tank provided by an embodiment of the present invention;
FIG. 6 is a first input shaft cross-sectional view provided by an embodiment of the present invention;
FIG. 7 is a partial view of an on-hook mechanical drive mechanism provided by an embodiment of the present invention;
fig. 8 is a partial view of the front and rear wheel drive mechanisms provided by an embodiment of the present invention.
Detailed Description
The present invention will be described in detail below with reference to the accompanying drawings.
In the description of the present invention, it should be noted that the directions or positional relationships indicated by the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. are based on the directions or positional relationships shown in the drawings, are merely for convenience of describing the present invention and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
As shown in fig. 1-8, an embodiment of the present invention provides a powershift transmission comprising a clutch transmission 10, a shift transmission 20, and a power take off mechanism 30; the clutch transmission mechanism 10 comprises a first input shaft 11 and a first output shaft 12, and the gear shifting transmission mechanism 20 comprises a second input shaft 21 and a second output shaft 22; the first input shaft 11 is in transmission fit with an engine output shaft, the first output shaft 12 is in transmission fit with the second input shaft 21, the second output shaft 22 is in transmission fit with the power output mechanism 30, and the clutch transmission mechanism 10 is assembled in such a way that the first input shaft 11 can drive the first output shaft 12 to switch between a forward rotation station and a reverse rotation station; the gear change transmission 20 is equipped such that the second input shaft 21 and the second output shaft 22 can be switched between a plurality of different gear ratios.
Preferably, the clutch transmission mechanism 10 further includes a housing 101, the first input shaft 11 and the first output shaft 12 are respectively rotatably disposed on bearing seats in the housing 101 through bearings, a first driving gear 13 and a second driving gear 14 are disposed on the first input shaft 11, wherein the first driving gear 13 is a single gear, and the second driving gear 14 is a duplex gear; the first output shaft 12 is provided with a first driven gear 15 and a second driven gear 16, wherein the first driven gear 15 is a duplex gear, the second driven gear 16 is a single gear, and the box 101 is also internally provided with a first transition gear 18; the first driving gear 13 is meshed with a left side gear of the first driven gear 15, the left side gear of the second driving gear 14 is meshed with a right side gear of the first driven gear 15, the right side gear of the second driving gear 14 is meshed with a first transition gear 18, and the first transition gear 18 is meshed with a second driven gear 16; the first driving gear 13 and the second driving gear 14 respectively form clutch transmission with the first input shaft 11 through a first hydraulic friction clutch 17a and a second hydraulic friction clutch 17b, and the first driven gear 15 and the second driven gear 16 respectively form clutch transmission with the first output shaft 12 through a third hydraulic friction clutch 17c and a fourth hydraulic friction clutch 17 d. The first output shaft 12 is in driving engagement with the second input shaft 21 via a pair of gears 40. The third and fourth hydraulic friction clutches 17c, 17d are used to control the forward and reverse rotation of the first output shaft 12, and the first and second hydraulic friction clutches 17a, 17b are used to control the gear ratio between the first input shaft 11 and the first output shaft 12.
Preferably, a first charging oil path 112, a second charging oil path 113 and a first lubricating oil path 111 are provided in the first input shaft 11 along a direction parallel to the axis, and the first charging oil path 112 and the second charging oil path 113 are respectively communicated with the piston cavities of the first hydraulic friction clutch 17a and the second hydraulic friction clutch 17b through charging holes provided radially or obliquely; the power input end of the first input shaft 11 protrudes to the outside of the box body 101, three annular oil grooves 114 are arranged on the shaft surface of the end, the three annular oil grooves 114 are respectively communicated with the first liquid filling oil way 112 and the second liquid filling oil way 113 and the first lubricating oil way 111 through radial through holes 107, a section of first sliding sleeve 104 matched with the shaft surface where the oil grooves are arranged is protruding and arranged on the outer side of the box body 101, three oil inlet holes which are respectively communicated with the three annular oil grooves 114 in a one-to-one correspondence mode are arranged on the first sliding sleeve 104, one oil inlet hole communicated with the first lubricating oil way 111 is connected with a lubricating oil supply pipeline through a pipeline, and two oil inlet holes communicated with the first liquid filling oil way 112 and the second liquid filling oil way 113 are respectively communicated with the electromagnetic valve 102 through pipelines.
Preferably, a third fluid-filled oil path, a fourth fluid-filled oil path and a second lubrication oil path are arranged in the first output shaft 12 along the direction parallel to the axis, and the two fluid-filled oil paths are respectively communicated with piston cavities of the third hydraulic friction clutch 17c and the fourth hydraulic friction clutch 17d through fluid-filled holes which are radially or obliquely arranged; one end of the first output shaft 12 protrudes to the outside of the box body 101, three annular oil grooves 114 are arranged on the shaft surface of the end, the three annular oil grooves 114 are respectively communicated with a third liquid filling oil way, a fourth liquid filling oil way and a second lubricating oil way through radial through holes 107, a second sliding sleeve 105 matched with the shaft surface where the oil grooves are arranged is protruding and arranged on the outer side of the box body 101, three oil inlet holes which are respectively communicated with the three annular oil grooves 114 in a one-to-one correspondence manner are arranged on the second sliding sleeve 105, one oil inlet hole communicated with the second lubricating oil way is connected with a lubricating oil supply pipeline through a pipeline, and two oil inlet holes communicated with the third liquid filling oil way and the fourth liquid filling oil way are respectively communicated with the electromagnetic valve 102 through pipelines.
Preferably, the first and second hydraulic friction clutches 17a and 17b are disposed corresponding to ring grooves between the left and right gears on the first driven gear 15; the third and fourth hydraulic friction clutches 17c and 17d are provided in correspondence with ring grooves between the left and right gears on the second driving gear 14.
Preferably, the solenoid valve 102 is mounted on a side wall of the case 101.
Preferably, a protruding rib is provided on the inner wall of the case 101, an integrated liquid filling oil path 103 is provided in the protruding rib, one end of the integrated liquid filling oil path 103 is communicated with the electromagnetic valve 102, and the other end is communicated to the end surfaces where the first sliding sleeve 104 and the second sliding sleeve 105 are located.
Preferably, a protruding rib is arranged on the inner wall of the box body 101, an integrated lubrication oil way is arranged in the protruding rib, one end of the integrated lubrication oil way is communicated with a lubrication pipe arranged on the outer wall of the box body 101, and the other end of the integrated lubrication oil way is communicated to the end face where the first sliding sleeve 104 and the second sliding sleeve 105 are located.
Preferably, the box 101 is a tubular structure with a front-back through structure, and comprises a cylindrical section for accommodating the coupling and a rectangular section for accommodating the first input shaft 11 and the first output shaft 12, a partition 106 is arranged between the cylindrical section and the rectangular section, one side of the partition 106, which is close to the cylindrical section, is an end surface where the first sliding sleeve 104 and the second sliding sleeve 105 are located, and a bearing seat for installing bearings of the first input shaft 11 and the first output shaft 12 is arranged on the partition 106.
Preferably, the axis of the cylindrical section is collinear with the axis of the first input shaft 11.
Preferably, a threaded hole 108 for connecting with the gear shifting transmission mechanism 20 shell is arranged at one end of the rectangular section far away from the cylindrical section, and a through hole 107 for the first input shaft 11 and the first output shaft 12 to protrude into the gear shifting transmission mechanism 20 shell is arranged on the end face.
Preferably, the first input shaft 11, the first output shaft 12 and the end of the rotating shaft of the first transition gear 18, which is far away from the cylindrical section, are all rotatably arranged in the housing of the gear shifting transmission mechanism 20 through bearings.
Preferably, a sealing ring groove is respectively arranged between two adjacent annular oil grooves 114 and outside the two annular oil grooves 114 at the two ends, and a sealing ring 115 is arranged in the sealing ring groove.
Preferably, the power output mechanism 30 includes a rear wheel driving mechanism 30a, a front wheel driving mechanism 30b, and an on-hook mechanical driving mechanism 30c, wherein the front wheel driving mechanism 30b and the on-hook mechanical driving mechanism 30c have a device capable of controlling the on-off of power.
Preferably, the rear wheel drive mechanism 30a includes a rear axle differential, and one end of the second output shaft 22 is in driving engagement with the rear axle differential via a bevel gear mechanism 39.
Preferably, the front wheel driving mechanism 30b includes a first output gear 32, a second transition gear 33, a second output gear 34, and a transition shaft 35; the first output gear 32 is rotationally connected with the second output shaft 22 synchronously, the second transition gear 33 is meshed with the first output gear 32, the second output gear 34 is meshed with the second transition gear 33, and the second output gear 34 and the first transition shaft 35 form clutch transmission fit through a fifth hydraulic friction clutch 36; the first transition shaft 35 is in transmission fit with a longitudinal transmission shaft 38 through a universal coupling 37, and the longitudinal transmission shaft 38 is in transmission fit with a front axle differential;
preferably, the externally hung mechanical driving mechanism 30c includes a third output shaft 31, a sixth hydraulic friction clutch 311, a second transition shaft 312, and an externally hung mechanical driving shaft 315, where the third output shaft 31 is rotationally connected with the first input shaft 11 synchronously, the second transition shaft 312 forms a clutch transmission fit with the third output shaft 31 through the sixth hydraulic friction clutch 311, and the externally hung mechanical driving shaft 315 and the second transition shaft 312 form a transmission fit with a variable transmission ratio.
Preferably, the second input shaft 21 has a hollow cylindrical structure, and the third output shaft 31 extends from the end of the first input shaft 11 to the right end of the housing of the gear shifting transmission mechanism 20 along the central hole of the second input shaft 21.
Preferably, the second transition shaft 312 has a hollow cylindrical structure, and the second transition shaft 312 is sleeved on the third output shaft 31 in a hollow manner.
Preferably, a third output gear 313 and a fourth output gear 314 are provided on the second transition shaft 312, and the third output gear 313 and the fourth output gear 314 are both connected with the second transition shaft 312 in a synchronous rotation manner; the externally hung mechanical driving shaft 315 is provided with a first speed-changing gear 316 and a second speed-changing gear 317, the first speed-changing gear 316 is meshed with the third output gear 313, and the second speed-changing gear 317 is meshed with the fourth output gear 314; the first speed-changing gear 316 and the second speed-changing gear 317 are sleeved on the externally hung mechanical driving shaft 315 in an empty mode, a gear hub 318 which is connected with the externally hung mechanical driving shaft 315 in a synchronous rotation mode is arranged between the first speed-changing gear 316 and the second speed-changing gear 317, auxiliary teeth which are flush with the tooth shape of the gear hub 318 are arranged on the side, opposite to the gear hub 318, of the first speed-changing gear 316 and the second speed-changing gear 317, a gear sleeve 319 is sleeved on the gear hub 318, the gear sleeve 319 and the gear hub 318 form sliding fit in the axis direction, and a shifting fork 310 used for driving the gear sleeve 319 to slide is arranged on the outer annular surface of the gear sleeve 319.
The foregoing description of the preferred embodiments of the invention is not intended to be limiting, but rather is intended to cover all modifications, equivalents, and alternatives falling within the spirit and principles of the invention.
Claims (5)
1. A power shift transmission system, characterized by: the device comprises a box body (101), a first input shaft (11) and a first output shaft (12), wherein the first input shaft (11) and the first output shaft (12) are respectively arranged on bearing seats in the box body (101) in a rotating mode through bearings, a first driving gear (13) and a second driving gear (14) are arranged on the first input shaft (11), the first driving gear (13) is a single gear, and the second driving gear (14) is a duplex gear; a first driven gear (15) and a second driven gear (16) are arranged on the first output shaft (12), wherein the first driven gear (15) is a duplex gear, the second driven gear (16) is a single gear, and a first transition gear (18) is also arranged in the box body (101); the first driving gear (13) is meshed with a left side gear of the first driven gear (15), the left side gear of the second driving gear (14) is meshed with a right side gear of the first driven gear (15), the right side gear of the second driving gear (14) is meshed with a first transition gear (18), and the first transition gear (18) is meshed with a second driven gear (16); the first driving gear (13) and the second driving gear (14) respectively form clutch transmission with the first input shaft (11) through a first hydraulic friction clutch (17 a) and a second hydraulic friction clutch (17 b), and the first driven gear (15) and the second driven gear (16) respectively form clutch transmission with the first output shaft (12) through a third hydraulic friction clutch (17 c) and a fourth hydraulic friction clutch (17 d);
a first liquid filling oil circuit (112), a second liquid filling oil circuit (113) and a first lubricating oil circuit (111) are arranged in the first input shaft (11) along the direction parallel to the axis, and the first liquid filling oil circuit (112) and the second liquid filling oil circuit (113) are respectively communicated with piston cavities of the first hydraulic friction clutch (17 a) and the second hydraulic friction clutch (17 b) through liquid filling holes which are radially or obliquely arranged; the power input end of the first input shaft (11) protrudes to the outside of the box body (101), three annular oil grooves (114) are formed in the shaft surface of the power input end, the three annular oil grooves (114) are respectively communicated with the first liquid filling oil way (112) and the second liquid filling oil way (113) and the first lubricating oil way (111) through radial through holes, a section of first sliding sleeve (104) matched with the shaft surface where the oil grooves are located is protruding and arranged on the outer side of the box body (101), three oil inlet holes which are respectively communicated with the three annular oil grooves (114) in a one-to-one correspondence mode are formed in the first sliding sleeve (104), one oil inlet hole which is communicated with the first lubricating oil way (111) is connected with a lubricating oil supply pipeline through a pipeline, and two oil inlet holes which are communicated with the first liquid filling oil way (112) and the second liquid filling oil way (113) are respectively communicated with the electromagnetic valve (102) through pipelines;
a third fluid-filled oil circuit, a fourth fluid-filled oil circuit and a second lubricating oil circuit are arranged in the first output shaft (12) along the direction parallel to the axis, and the two fluid-filled oil circuits are respectively communicated with piston cavities of the third hydraulic friction clutch (17 c) and the fourth hydraulic friction clutch (17 d) through fluid-filled holes which are radially or obliquely arranged; one end of the first output shaft (12) protrudes out of the box body (101), three annular oil grooves are formed in the shaft face of the end, the three annular oil grooves are respectively communicated with a third liquid filling oil way, a fourth liquid filling oil way and a second lubricating oil way through radial through holes, a second sliding sleeve (105) matched with the shaft face where the oil grooves are located is arranged on the outer side of the box body (101) in a protruding mode, three oil inlet holes which are respectively communicated with the three annular oil grooves in a one-to-one correspondence mode are formed in the second sliding sleeve (105), one oil inlet hole which is communicated with the second lubricating oil way is connected with a lubricating oil supply pipeline through a pipeline, and two oil inlet holes which are communicated with the third liquid filling oil way and the fourth liquid filling oil way are respectively communicated with the electromagnetic valve (102) through pipelines;
the first and second hydraulic friction clutches (17 a, 17 b) are correspondingly arranged with annular grooves between the left and right gears on the first driven gear (15); the third and fourth hydraulic friction clutches (17 c, 17 d) are provided in correspondence with ring grooves between the left and right gears on the second drive gear (14).
2. The powershift transmission system of claim 1, wherein: the electromagnetic valve (102) is arranged on the side wall of the box body (101).
3. The powershift transmission system of claim 2, wherein: the inner wall of the box body (101) is provided with a convex rib, an integrated liquid filling oil way (103) is arranged in the convex rib, one end of the integrated liquid filling oil way (103) is communicated with the electromagnetic valve (102), and the other end of the integrated liquid filling oil way is communicated to the end faces where the first sliding sleeve (104) and the second sliding sleeve (105) are located.
4. The powershift transmission system of claim 2, wherein: the inner wall of the box body (101) is provided with a convex rib, an integrated lubricating oil way is arranged in the convex rib, one end of the integrated lubricating oil way is communicated with a lubricating joint pipe arranged on the outer wall of the box body (101), and the other end of the integrated lubricating oil way is communicated to the end faces where the first sliding sleeve (104) and the second sliding sleeve (105) are located.
5. The powershift transmission system of claim 1, wherein: and sealing ring grooves are respectively arranged between two adjacent annular oil grooves (114) and outside the two annular oil grooves (114) at the two ends, and sealing rings (115) are arranged in the sealing ring grooves.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711222479.3A CN107781360B (en) | 2017-11-29 | 2017-11-29 | power shift transmission system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711222479.3A CN107781360B (en) | 2017-11-29 | 2017-11-29 | power shift transmission system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107781360A CN107781360A (en) | 2018-03-09 |
| CN107781360B true CN107781360B (en) | 2023-12-05 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201711222479.3A Active CN107781360B (en) | 2017-11-29 | 2017-11-29 | power shift transmission system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN107781360B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110345206B (en) * | 2019-08-09 | 2024-07-09 | 滁州悦达实业有限公司 | Gearbox steering adjusting device |
| CN110985627B (en) * | 2019-12-04 | 2022-03-04 | 西南大学 | Mechanical double-overrunning self-adaptive automatic transmission adopting multi-row floating overrunning clutch |
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- 2017-11-29 CN CN201711222479.3A patent/CN107781360B/en active Active
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|---|---|---|---|---|
| GB1003911A (en) * | 1960-10-11 | 1965-09-08 | Massey Ferguson Ltd | Improvements in relating to variable speed gears |
| US3412625A (en) * | 1966-05-19 | 1968-11-26 | Eaton Yale & Towne | Transmission system |
| CN86103135A (en) * | 1985-05-13 | 1986-11-26 | 伊顿公司 | Semiautomatic gearbox |
| CN2649874Y (en) * | 2003-09-29 | 2004-10-20 | 重庆齿轮箱有限责任公司 | Change speed gear box for oil drilling |
| CN101907153A (en) * | 2009-06-07 | 2010-12-08 | 陈安模 | Intelligent continuously variable transmission of automobile |
| CN102652235A (en) * | 2009-12-31 | 2012-08-29 | 博格华纳公司 | Automatic transmission having high pressure actuation and low pressure lube hydraulic circuit |
| CN204114031U (en) * | 2014-09-28 | 2015-01-21 | 中国第一汽车股份有限公司 | A kind of novel double-clutch automatic transmission layout |
| CN205101479U (en) * | 2015-09-30 | 2016-03-23 | 重庆隆旺机电有限责任公司 | Modular derailleur assembly |
| CN105485265A (en) * | 2015-12-28 | 2016-04-13 | 北京理工大学 | Multi-gear power gear shifting parallel hybrid power gearbox |
| CN207514162U (en) * | 2017-11-29 | 2018-06-19 | 滁州悦达实业有限公司 | Power shifting transmission system |
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| CN107781360A (en) | 2018-03-09 |
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